EP3859159B1 - Schraubenverdichter - Google Patents

Schraubenverdichter Download PDF

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Publication number
EP3859159B1
EP3859159B1 EP21163537.0A EP21163537A EP3859159B1 EP 3859159 B1 EP3859159 B1 EP 3859159B1 EP 21163537 A EP21163537 A EP 21163537A EP 3859159 B1 EP3859159 B1 EP 3859159B1
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EP
European Patent Office
Prior art keywords
control
slider
compressor according
screw compressor
gap
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21163537.0A
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German (de)
English (en)
French (fr)
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EP3859159A1 (de
Inventor
Tihomir Mikulic
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to EP21163537.0A priority Critical patent/EP3859159B1/de
Publication of EP3859159A1 publication Critical patent/EP3859159A1/de
Application granted granted Critical
Publication of EP3859159B1 publication Critical patent/EP3859159B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/185—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the invention relates to a screw compressor comprising a compressor housing with a screw rotor space arranged therein, two screw rotors arranged in the screw rotor space and each rotatably mounted on the compressor housing about a screw rotor axis, which interlock with their screw contours and each interact with compression wall surfaces adjacent to and partially surrounding them in order to receive gaseous medium supplied via a low-pressure chamber arranged in the compressor housing and to release it in the area of a high-pressure chamber arranged in the compressor housing, the gaseous medium being enclosed in compression chambers formed between the screw contours and compression wall surfaces adjacent thereto with a suction volume at low pressure and compressed to a final volume at high pressure is, as well as two control slides arranged one behind the other in a slide channel of the compressor housing in a displacement direction running parallel to the screw rotor axes and adjacent to both screw rotors with slide compression wall surfaces, which are movable in the displacement direction, a first control slide being arranged to influence the final volume and a second control
  • Such screw compressors are from the prior art, such as US4516914 and JPH09-317676 , known.
  • control slides are designed at their mutually facing end regions in such a way that during a transition from the connected position to the separated position, a first throttle gap with a gap width running transversely to the direction of displacement is formed in a first transition position following the connected position and that the first throttle gap is arranged offset in the displacement direction relative to the mutually facing end faces of the control slides.
  • Such a first throttle gap creates the possibility for the medium exiting the compression chamber to enter the space between the control slides in a throttled manner and the possibility of forming the throttle gap independently of the gap forming between the end faces.
  • the first throttle gap in the first transition position has a smaller gap width than the gap that forms between the end faces of the control slides, so that the outflow of the medium can be defined exclusively by the throttle gap and thus the possibility is created in which defined the first transitional position To provide flow conditions for the outflowing medium.
  • the first throttle gap with its gap width is present over a path in the displacement direction that is larger than the gap width of the throttle gap, so that the first transition position can be realized over a significant, defined distance in the displacement direction.
  • the first throttle gap can be designed in a wide variety of ways.
  • the first throttle gap is delimited by two wall surfaces, one of which is arranged at the end region of the first control slide and the other at the end region of the second control slide.
  • the wall surfaces are preferably located such that the wall surface formed by the end region of the first control slide runs adjacent to the end face of the first control slide.
  • the wall surface arranged at the end region of the second control slide runs adjacent to the end face of the second control slide.
  • An advantageous solution provides that at least one of the wall surfaces runs essentially parallel to the direction of displacement.
  • a substantially parallel course to the direction of displacement is understood to mean that the deviation from a parallel course is a maximum of ⁇ 20°.
  • both wall surfaces run essentially parallel to the displacement direction, so that the gap width does not vary during a movement in the displacement direction in the first transition position.
  • control slides are designed at their mutually facing end regions in such a way that in a second transition position lying between the first transition position and the separation position, a second throttle gap is formed with a gap width that runs transversely to the direction of displacement and is larger than that Gap width of the first throttle gap.
  • the second throttle gap is arranged so that it is delimited by at least one wall surface, which is arranged on a side of the wall surface delimiting the first throttle gap facing away from the end face.
  • this wall surface is set back from the wall surface of this control body delimiting the first throttle gap in order to achieve a larger gap width.
  • the second throttle gap is delimited by a wall surface which also delimits the first throttle gap.
  • a further advantageous embodiment provides that at least one of the end faces of the control slides has a sealing edge surface adjacent to the slide compression wall surfaces and, on a side of the sealing edge surface opposite the slide compression wall surfaces, an inner surface which is adjacent to the sealing edge surface and is recessed or lowered relative to the sealing edge surface in the direction parallel to the displacement direction.
  • This solution has the advantage that, firstly, the sealing edge surface of one end face can form a seal with the other end face in the connected position and, on the other hand, the recessed or lowered inner surface is available to build up a force which helps to move the control slides apart.
  • the sealing edge surface extends so far in the direction of the slide channel that it still adjoins a partial surface of the guide circumferential surface of the respective control slide, so that a reliable seal is achieved by the sealing edge surface with the opposite end face of the other control slide is guaranteed.
  • the inner surface set back from the sealing edge surface forms a gap space with the opposite end face in the connected position of the control slides, which is connected to an inflow space delimited by the control slides in the connected position and is at the same pressure level as the inflow space, so that a force that is already effective in the connected position can be generated, which supports the control slides moving apart.
  • the inflow space is at low pressure in the connected position of the control slides.
  • two screw rotors 26, 28 are provided in a screw rotor space 18 of the compressor housing 12, each rotatable about a screw rotor axis 22, 24, which engage with one another with their screw contours 32 and 34 and cooperate with compression wall surfaces 36 and 38 of the screw rotor space 18 adjacent to them on the circumference, in order to receive a gaseous medium supplied to a low-pressure space 42 adjacent to the screw contours 32, 34 on the suction side, to compress it and to release it into a high-pressure space 44 in the compressor housing 12 at high pressure.
  • the gaseous medium in particular refrigerant, is enclosed in a suction volume at low pressure in compression chambers formed between the screw contours 32, 34 and the compression wall surfaces 36, 38 adjacent to them and is compressed to a final volume at high pressure.
  • the operating state of the screw compressor 10 is adapted on the one hand with regard to the volume ratio, which indicates the relationship between the maximum enclosed suction volume and the final volume pushed out, and on the other hand with regard to the compressor performance, which indicates the proportion of the volume flow actually compressed by the screw compressor based on the maximum volume flow that can be compressed by the screw compressor 10.
  • a first control slide 52 and a second control slide 54 are arranged one behind the other in a slide channel 56 provided in the compressor housing 12, the slide channel 56 running parallel to the screw rotor axes 22, 24 and the first Control slide 52 and the second control slide 54 in the area of their guide peripheral surface 58 that is not adjacent to the screw rotors 26, 28 in a displacement direction 72 defined by the slide channel 56.
  • the first control slide 52 faces the high-pressure chamber 44 and is therefore arranged on the high-pressure side and the second control slide 54 is arranged on the low-pressure side relative to the first control slide 52.
  • Each of the two control slides 52 and 54 also has a slide compression wall surface 62 adjacent to the screw rotor 26 and a slide compression wall surface 64 adjacent to the screw rotor 28, which represent partial areas of the compression wall surfaces 36 and 38, and housing compression wall surfaces 66 and 68 formed by the compressor housing 12, which also Partial surfaces of the compression wall surfaces 36 and 38 represent the compression wall surfaces 36 and 38, which together with the screw contours 32 and 34 contribute to the formation of the compression chambers.
  • the first control slide 52 and the second control slide 54 are, as in Fig. 2 to 15 shown, designed so that they are identical insofar as they form the slide compression wall surfaces 62 and 64 as well as the guide peripheral surface 58 and thus they can be guided displaceably in the slide channel 56 of the compressor housing 12 in a single displacement direction 72 running parallel to the screw rotor axes 22, 24 .
  • the first control slide 52 forms an outlet edge 82 that faces the high-pressure chamber 44 and defines the end volume of the compression chambers Compression chambers and thus the volume ratio are determined.
  • first control slide 52 and the second control slide 54 have end faces 86 and 88 which adjoin the slide compression wall surfaces 62, 64 and run transversely thereto and face one another, with which these, as for example in Fig. 4 shown, can be placed against one another in such a way that the slide compression wall surfaces 62 and 64 of the first control slide 52 and the second control slide 54 merge into one another.
  • a compression spring 104 is preferably provided, which serves to act on the first control slide 52 relative to the second control slide 54 so that the end faces 86 and 88 can be moved away from one another.
  • a cylinder arrangement 112 which comprises a cylinder chamber 114 and a piston 116, the piston 116 being connected to a piston rod 118, which establishes a connection to the first control slide 52, for example with an in Fig. 2 and Fig. 4 shown extension 122 of the first control slide 52, which is arranged, for example, on a side of the same opposite the end face 86.
  • the cylinder arrangement 112 lies in particular on a side of the first control slide 52 opposite the second control slide 54, preferably in a high-pressure side housing section 124 of the compressor housing 12, which is connected to the slide channel 56 and connected to the high-pressure chamber 44 and thus on a low-pressure chamber 42 opposite side of the compressor housing 12 is arranged.
  • the second control slide 54 is displaceable by a cylinder arrangement 132, which comprises a piston 136 movable in a cylinder chamber 134, the cylinder chamber 134 extending in particular as a continuation of the slide channel 56 in a low-pressure side housing section 142, in which, for example, drive-side bearing units for the screw rotors 26 and 28 are arranged, which can be driven, for example, via a drive shaft 143.
  • a cylinder arrangement 132 which comprises a piston 136 movable in a cylinder chamber 134, the cylinder chamber 134 extending in particular as a continuation of the slide channel 56 in a low-pressure side housing section 142, in which, for example, drive-side bearing units for the screw rotors 26 and 28 are arranged, which can be driven, for example, via a drive shaft 143.
  • the piston 136 is integrally formed on the second control slide 54 and has a piston surface that corresponds at least to the cross-sectional area of the second control slide 54.
  • the low-pressure side housing section 142 which accommodates the cylinder chamber 134 for the cylinder arrangement 132 for moving the second control slide 54, lies in an area of the compressor housing 12 which is arranged opposite the high-pressure side housing section 124 for receiving the cylinder chamber 114 for the cylinder arrangement 112.
  • the first control slide 52 and the second control slide 54 can be pushed together by the cylinder arrangements 112 and 132 to such an extent that the end faces 86 and 88 rest against one another in a connected position, and the two control slides 52, 54 can also be pushed together like a single control slide in the connected position move, which extends from the suction-side end surface 126 in the direction of the pressure-side end surface 84 and whose outlet edge 82 contributes to determining the volume ratio, whereby, as in Fig. 4 and Fig. 6 shown, the screw compressor 10 always promotes the maximum volume flow in this composite position.
  • the volume ratio can be adjusted, starting from that in the position according to Fig. 4 present minimum value with increasingly smaller distance the outlet edge 82 rises from the end surface 84 and reaches its maximum value when the outlet edge 82 has the smallest distance from the end surface 84 required to minimize the final volume, as for example in Fig. 6 shown.
  • the second control slide 54 is ineffective, since the medium to be compressed flows from the compression chamber above the end faces 86 and 88 between the control slides 52, 54 in the direction of the slide channel 56, which is connected to the low-pressure chamber 42 on the side of the slide channel 56 in the compressor housing 12 arranged outflow openings 144 ( Fig. 2 ) and adjoining channels in the compressor housing 12 are connected.
  • Opposite outflow openings 144 are preferably arranged on opposite longitudinal sides of the slide channel 56.
  • the outflow openings 144 extend in particular over a region of the slide channel 12, which extends from the suction-side end surface 126 in the direction of the pressure-side end surface 84.
  • the position of the end face 86 of the first control slide 52 determines the initial volume.
  • the outlet edge 82 is not in a position in which it specifies the minimum possible final volume, the relation of the initial volume, determined by the end face 86, to the final volume, determined by the outlet edge 82, is not variable.
  • the second control slide 54 In order to eliminate the effect of the second control slide 54 in the disconnected position, it is retracted into the housing section 142 in particular by means of the cylinder arrangement 132, the cylinder chamber 134 being dimensioned such that it simultaneously includes an retraction space 148 for the second control slide 54 and thus the possibility manages to move the second control slide 54 so far away from the first control slide 52 that the end face 88 no longer influences the initial volume.
  • the second control slide 54 thus allows the initial volume to be influenced by either resting with its end face 88 on the end face 86 of the first control slide 52 to form the connected position of the control slides 52, 54 and thus maximizing the initial volume or with its own end face 88 can be moved far away from the end face 86 of the first control slide 52 so that the initial volume is no longer influenced by the second control slide 54.
  • control slides 52, 54 are stepped at their mutually facing end regions 152, 154, the second control slide 54 having an extension 164 which carries the slide compression wall surfaces 62, 64 and the end face 88 and thus adjoins the screw contours 32, 34, while the first control slide 52 has an extension 162 which projects beyond the end face 86 in the direction of the second control slide 54 and which in particular lies essentially in the slide channel 56.
  • the extensions 164 and 162 are preferably designed so that in the in Fig. 4 and Fig. 6 In the illustrated composite position, the extension 164 engages over the extension 162 in such a way that the end faces 88 and 86 of the control slides 54 and 52 rest against one another in a sealing manner and the slide compression wall surfaces 62, 64 merge into one another.
  • extension 164 in particular is designed in such a way that it still includes partial surfaces 172 of the guide peripheral surface 58 of the second control slide 54 which adjoin the slide compression wall surfaces 62, 64 and the end face 68, so that the extension 164 in turn is also guided in the slide channel 56 ( Fig. 9 ).
  • extension 162 in turn forms a partial surface 174 that supplements the partial surfaces 172 in the circumferential direction to the peripheral surface 58.
  • the extension 162 further comprises a cylindrical extension 176, which, for example, in Fig. 4 and 6 shown, forms a receptacle 178 for the compression spring 104, which extends from this receptacle 178 to a support flange 182 of a central recess 184 provided in the second control slide 54 and with a force acting on the control slides 52 that moves the control slides 52, 54 away from each other , 54 acts.
  • a cylindrical extension 176 which, for example, in Fig. 4 and 6 shown, forms a receptacle 178 for the compression spring 104, which extends from this receptacle 178 to a support flange 182 of a central recess 184 provided in the second control slide 54 and with a force acting on the control slides 52 that moves the control slides 52, 54 away from each other , 54 acts.
  • first throttle gap 196 in a first transition position that occurs during the transition from the connected position to the separated position a first gap width SB1 running transversely to the displacement direction 72, which, as in Fig. 7 and particularly Fig. 8 shown, an inflow of the medium to be compressed into an inflow space 198 throttles, which forms the central recess 184 in the second control slide 54 and a transverse by moving from the connected position towards the separation position already in the first transition position between the control slides 52, 54 includes space 202 limited to the direction of displacement by the slide channel 56.
  • the second control slide 54 is provided with outflow outlets 212, in particular outflow windows 212, in the area of its side walls 214 forming the guide peripheral surfaces 58, which are in the central recess 184 delimiting side walls 214 of the second control slide 54 are arranged ( Fig. 7 , 9 to 11 ), wherein the outflow outlets 212 are positioned so that they are arranged to overlap with the side outflow openings 144 in the first transition position.
  • the extent of the gap 202 in the displacement direction 72 is so small that it does not overlap with the outflow openings 144 or to a significant extent.
  • the first throttle gap 196 is decisive for throttling the outflowing medium.
  • first throttle gap 196 formed between the first wall surfaces 192 and 194 of the extensions 162, 164 is ineffective, and a second throttle gap 222 is formed with a second gap width SB2 running transversely to the displacement direction 72 and with a larger cross section than the first throttle gap 196 between the wall surface 194 of the extension 164 and a wall surface 224 of the first extension 162 that is set back from the wall surface 192.
  • the outflow outlets 212 are arranged to overlap with the outflow openings 144, so that the second throttle gap 222 is decisive for throttling the outflowing medium.
  • the end face 88 is provided with a sealing edge surface 232 adjacent to the slide compression wall surfaces 62, 64 and the partial surface 172 of the guide peripheral surface 58, relative to which an inner surface 234 runs set back or lowered, so that between this inner surface 234 and the end face 86 creates a gap space 236 in which medium under low pressure is present even in the connected position of the control slides 52, 54, so that the inner surface 234 acted upon by the low pressure and the partial area of the end face 86 facing it counteract the cylinder arrangements 112 and 132 forces that promote the transition from the connected position to the separated position and thus make it more reliable ( Fig. 9 to 11 ).
  • a position detection device designated as a whole 252 which comprises a detector element 254 extending parallel to the displacement direction 72 of the control slides 52, 54 and thus parallel to the screw rotor axes 22, 24, which is capable of detecting the positions of position indicator elements 256 and 258.
  • the position display element 256 is firmly coupled to the first control slide 52, namely with the extension 162 of the first control slide 52, and the position display element 258 is coupled to the second control slide 54, namely with the one in the slide channel 56 and the first control slide 52 facing end region 154 of the same, as in particular in Fig. 15 shown.
  • each of these position display elements 256 and 258 comprises a fork body, designated as a whole by 274, which, with its two fork legs 276 and 278, delimits an intermediate space 282 between them, through which the elongated detector element 254 runs.
  • Each of these fork bodies 274 is coupled to the corresponding control slide 52, 54 via a connecting body 272 connected to the extension 162 or the end region 154 ( Fig. 15 ).
  • the connecting bodies 272 which are held on the respective control slides 52, 54, pass through an elongated, slot-shaped passage 294, which is formed into a housing wall 296 forming the slide channel 56 and has a length which allows the second control slide 54 to be completely retracted in the disconnected position into the retraction space 148 and a position of the first control slide 52 at a minimum initial volume and a position of the first control slide 52 at a minimum volume ratio, that is to say a maximum distance of the outlet edge 82 from the pressure-side end surface 84, and also in the connected position a position of the second control slide 54 with the first control slide 52 at maximum volume ratio and minimum volume ratio.
  • the passage 294 is always kept at the pressure in the low-pressure chamber 42 and thus also serves to keep the control slides 52, 54 with their guide peripheral surface 58 in contact with the slide channel 56, so that the control slides 52, 54 do not slip between the slide channel 56 and the guide peripheral surface 58 forming high pressure with the slide compression wall surfaces 62, 64 can press against the screw rotors 26, 28.
  • the passage 294 is sealed against higher pressures, in particular high pressure, by the narrowly tolerable gap between the slide channel 56 and the guide peripheral surface 58 of the control slides 52, 54.
  • a controller 318 is provided, which, through the connection to the position detection device 252, is able to determine the actual positions of the control slides 52, 54.
  • the cylinder arrangements 112 and 132 can be controlled with the control 318 in order to position the control slides 52, 54.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP21163537.0A 2016-04-06 2016-04-06 Schraubenverdichter Active EP3859159B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21163537.0A EP3859159B1 (de) 2016-04-06 2016-04-06 Schraubenverdichter

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
PCT/EP2016/057534 WO2017174130A1 (de) 2016-04-06 2016-04-06 Schraubenverdichter
EP16714450.0A EP3440358B9 (de) 2016-04-06 2016-04-06 Schraubenverdichter
EP21163537.0A EP3859159B1 (de) 2016-04-06 2016-04-06 Schraubenverdichter

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP16714450.0A Division EP3440358B9 (de) 2016-04-06 2016-04-06 Schraubenverdichter
EP16714450.0A Division-Into EP3440358B9 (de) 2016-04-06 2016-04-06 Schraubenverdichter

Publications (2)

Publication Number Publication Date
EP3859159A1 EP3859159A1 (de) 2021-08-04
EP3859159B1 true EP3859159B1 (de) 2024-03-27

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EP21163537.0A Active EP3859159B1 (de) 2016-04-06 2016-04-06 Schraubenverdichter
EP16714450.0A Active EP3440358B9 (de) 2016-04-06 2016-04-06 Schraubenverdichter

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EP16714450.0A Active EP3440358B9 (de) 2016-04-06 2016-04-06 Schraubenverdichter

Country Status (5)

Country Link
US (1) US11286935B2 (zh)
EP (2) EP3859159B1 (zh)
CN (1) CN109072919B (zh)
RU (1) RU2713784C1 (zh)
WO (1) WO2017174130A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6500964B1 (ja) * 2017-10-30 2019-04-17 ダイキン工業株式会社 スクリュー圧縮機

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4516914A (en) * 1982-09-10 1985-05-14 Frick Company Micro-processor control of moveable slide stop and a moveable slide valve in a helical screw rotary compressor
JPS59188076A (ja) * 1984-03-23 1984-10-25 Kobe Steel Ltd スライド弁式スクリユ圧縮機
US5183395A (en) 1992-03-13 1993-02-02 Vilter Manufacturing Corporation Compressor slide valve control
JPH09317676A (ja) * 1996-05-23 1997-12-09 Hitachi Ltd スクリュー圧縮機の容量制御装置
DK1963678T3 (da) * 2005-12-12 2011-10-31 Johnson Controls Denmark Aps Skruekompressor
US7891955B2 (en) * 2007-02-22 2011-02-22 Vilter Manufacturing Llc Compressor having a dual slide valve assembly
US8813492B2 (en) * 2009-10-14 2014-08-26 Hansen Engine Corporation Internal combustion engine and supercharger
RU2418193C1 (ru) * 2009-10-27 2011-05-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Винтовой компрессор с регулятором производительности
CN203257685U (zh) * 2012-12-26 2013-10-30 福建雪人压缩机科技有限公司 机械式高精度螺杆压缩机能量及内容积比滑阀调节机构
DE102015116324A1 (de) * 2014-10-08 2016-04-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
EP4245997A3 (de) * 2016-04-06 2023-12-27 BITZER Kühlmaschinenbau GmbH Verdichtereinheit und verfahren zum betreiben einer verdichtereinheit

Also Published As

Publication number Publication date
CN109072919B (zh) 2020-05-12
CN109072919A (zh) 2018-12-21
EP3440358A1 (de) 2019-02-13
US11286935B2 (en) 2022-03-29
EP3440358B9 (de) 2022-03-23
EP3440358B1 (de) 2021-03-24
US20190032661A1 (en) 2019-01-31
EP3859159A1 (de) 2021-08-04
RU2713784C1 (ru) 2020-02-07
WO2017174130A1 (de) 2017-10-12

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